JPWO2018189892A1 - Distributor, heat exchanger, and refrigeration cycle device - Google Patents

Abstract

Provided is a distributor capable of distributing an appropriate amount of refrigerant even in a downstream branch flow path. A distributor (2) for distributing a fluid flowing from a fluid inlet portion (12a_1) to a plurality of fluid outlet portions (12a_3), comprising a plurality of upstream branch flow paths (12a_2) and a plurality of upstream branch flow paths. A plurality of branch flow paths having a downstream branch flow (12a_3) at the fluid outlet side, and between the upstream branch flow path and the downstream branch flow path; And an intermediate flow path (13a_2) connecting the flow path and the flow path. The intermediate flow path is connected to one end (120) connected to the upstream branch flow path and to the downstream branch flow path. And the other end (121), which changes the direction of the fluid flowing from one end and then flows out from the other end.

Description

  The present invention relates to a distributor, a heat exchanger, and a refrigeration cycle device used for a heat circuit and the like.

The heat exchanger has a flow path (path) in which a plurality of heat transfer tubes are arranged in parallel in order to reduce the pressure loss of the refrigerant flowing in the heat transfer tubes. At the refrigerant inlet of each heat transfer tube, for example, a header or a distributor, which is a distributor for evenly distributing the refrigerant to each heat transfer tube, is arranged.
It is important to evenly distribute the refrigerant to the plurality of heat transfer tubes in order to ensure the heat transfer performance of the heat exchanger.

As such a distributor, for example, by laminating a plurality of plate-like bodies, a distribution channel that branches into a plurality of outlet channels with respect to one inlet channel is formed, and each transfer of the heat exchanger is performed. A device that distributes and supplies a coolant to a heat pipe has been proposed (for example, see Patent Document 1).
The distributor described in Patent Literature 1 is configured by alternately stacking a bare material that is a plate-shaped body not coated with a brazing material and a clad material that is a plate-shaped body coated with a brazing material. The distribution passage is formed by connecting the formed circular through hole and the substantially Z-shaped through groove.

International Publication No. WO 2016/071946

  In the distributor described in Patent Literature 1, both ends of a substantially Z-shaped through groove (hereinafter, referred to as an upstream branch flow path) formed on the upstream side have a substantially Z-shaped shape formed on the downstream side. It is formed at the same height position in the direction of gravity as the branch point (central portion) of the through groove (hereinafter referred to as the downstream branch flow path). For this reason, it is conceivable that the bias of the liquid film at the end of the upstream branch flow passage affects the refrigerant distribution at the branch point of the downstream branch flow passage.

  If it is assumed that the liquid film is significantly biased, it is expected that it will be difficult to set the distribution ratio of the refrigerant at the branch point of the downstream branch flow passage to a predetermined amount (target value). In other words, the closer to the downstream branch flow path, the more difficult it is to adjust the distribution ratio of the refrigerant. As a result, an appropriate amount of refrigerant cannot flow through the heat exchanger, heat exchange efficiency is reduced, and operation efficiency of the refrigeration cycle may be reduced.

  The present invention has been made in view of the above problems, and provides a distributor, a heat exchanger, and a refrigeration cycle apparatus that can distribute an appropriate amount of refrigerant even in a downstream branch flow path. The purpose is to do.

  The distributor according to the present invention is a distributor that distributes a fluid flowing from a fluid inlet to a plurality of fluid outlets, and includes an upstream branch flow path and a plurality of fluid outlets more than the upstream branch flow path. A plurality of branch flow paths having a downstream branch flow path on the side, and between the upstream branch flow path and the downstream branch flow path, wherein the upstream branch flow path and the downstream branch flow And an intermediate flow path connecting the flow path, and the intermediate flow path has one end connected to the upstream branch flow path and the other end connected to the downstream branch flow path. And an end, wherein the flow of the fluid that has flowed in from the one end is changed in direction and then flows out from the other end.

A heat exchanger according to the present invention includes the distributor described above, and a plurality of heat transfer tubes into which the fluid flowing out of the plurality of fluid outlets of the distributor flows.
A refrigeration cycle device according to the present invention includes the above heat exchanger as at least one of an evaporator and a condenser.

According to the distributor according to the present invention, since the intermediate flow path changes the direction of the fluid flowing from one end and flows out from the other end, the intermediate flow path branches from the upstream branch flow path to the downstream branch flow. It is possible for the fluid to branch off in a state where the fluid is homogeneously mixed without the fluid flowing straight into the flow path.
Since the heat exchanger according to the present invention has the distributor described above, the fluid can flow in a homogeneous state, and the heat exchange efficiency is improved.
Since the refrigeration cycle device according to the present invention has the above-described heat exchanger, the refrigerant can flow in a uniform state in each path in the heat exchanger, and maximize the performance of the heat exchanger. Becomes possible.

It is a figure which shows roughly the structure of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view in the state where the distributor concerning Embodiment 1 of the present invention was disassembled. FIG. 2 is a development view of the distributor according to Embodiment 1 of the present invention. FIG. 2 is a longitudinal sectional view of the distributor according to Embodiment 1 of the present invention. It is an exploded perspective view for explaining the flow of the refrigerant in the conventional distributor as a comparative example. It is a schematic diagram for explaining the flow of the refrigerant in the conventional distributor as a comparative example. FIG. 3 is an exploded perspective view for describing a flow of a refrigerant in a distributor according to the first embodiment of the present invention. FIG. 3 is a schematic diagram for explaining a flow of a refrigerant in a distributor according to the first embodiment of the present invention. FIG. 3 is a diagram illustrating a flow of a method of manufacturing the heat exchanger according to Embodiment 1 of the present invention. It is a longitudinal cross-sectional view of the distributor according to Embodiment 1 of the present invention using the lost wax method. FIG. 10 is a longitudinal sectional view illustrating the flow of the refrigerant in the distributor according to Embodiment 1 of the present invention completed by the manufacturing method of FIG. 9. FIG. 9 is an exploded perspective view for explaining a flow of a refrigerant in a distributor according to Embodiment 2 of the present invention. It is a schematic diagram for explaining the flow of the refrigerant in the distributor according to Embodiment 2 of the present invention. FIG. 11 is an exploded perspective view for explaining a flow of a refrigerant in a distributor according to Embodiment 3 of the present invention. It is a schematic diagram which shows typically the shape of the through-hole formed in the 1st plate-shaped member of the distributor which concerns on Embodiment 3 of this invention. FIG. 14 is a circuit configuration diagram schematically illustrating an example of a refrigerant circuit configuration of a refrigeration cycle device according to Embodiment 4 of the present invention.

Hereinafter, a distributor, a heat exchanger, and a refrigeration cycle device according to the present invention will be described with reference to the drawings.
Note that the configuration, operation, and the like described below are merely examples, and the distributor, the heat exchanger, and the refrigeration cycle device according to the present invention are not limited to such a configuration, operation, and the like. Further, in each of the drawings, the same or similar components are denoted by the same reference numerals, or the reference numerals are omitted. The illustration of the detailed structure is appropriately simplified or omitted. Further, overlapping or similar descriptions are simplified or omitted as appropriate.

  In the following, the case where the distributor according to the present invention and the heat exchanger are applied to an air conditioner that is an example of a refrigeration cycle device is described, but is not limited to such a case. The present invention may be applied to other refrigeration cycle devices having a refrigerant circuit. Further, the case where the refrigeration cycle apparatus switches between the heating operation (heating operation) and the cooling operation (cooling operation) is described, but the present invention is not limited to such a case, and only the heating operation or the cooling operation is performed. It may be performed.

Embodiment 1 FIG.
A distributor and a heat exchanger according to Embodiment 1 of the present invention will be described.
<Configuration of heat exchanger 1>
Hereinafter, a schematic configuration of the heat exchanger 1 according to Embodiment 1 will be described.
FIG. 1 is a diagram schematically showing a configuration of a heat exchanger 1 according to the first embodiment. In FIG. 1, the flow direction of the fluid is indicated by black arrows. In the following, description will be made using a refrigerant as an example of the fluid.

  As shown in FIG. 1, the heat exchanger 1 includes a first distributor 2, a second distributor 3, a plurality of heat transfer tubes 4, and a plurality of fins 5. Note that the second distributor 3 may use the same type of distributor as the first distributor 2 or a different type of distributor from the first distributor 2.

Inside the first distributor 2, at least one distribution channel 2a is formed. A refrigerant pipe is connected to the inflow side of the distribution channel 2a. A plurality of heat transfer tubes 4 are connected to the outflow side of the distribution channel 2a.
The first distributor 2 corresponds to the “distributor” of the present invention.
A merging flow path 3a is formed inside the second distributor 3. A plurality of heat transfer tubes 4 are connected to the inflow side of the joining flow path 3a. A refrigerant pipe is connected to the outflow side of the joining flow path 3a.

The heat transfer tube 4 is a flat tube or a circular tube in which a plurality of flow paths are formed. The heat transfer tube 4 is made of, for example, aluminum. A plurality of fins 5 are joined to the heat transfer tube 4.
The fin 5 is made of, for example, aluminum. The heat transfer tubes 4 and the fins 5 are joined by, for example, brazing. Although FIG. 1 shows a case where the number of the heat transfer tubes 4 is four, the present invention is not limited to such a case. In the first embodiment, the case where the heat transfer tube 4 is a flat tube will be described as an example.

<Flow of refrigerant in heat exchanger>
Hereinafter, the flow of the refrigerant in the heat exchanger 1 will be described.
The refrigerant flowing through the refrigerant pipe flows into the first distributor 2, is distributed in the distribution channel 2 a, and flows out to the plurality of heat transfer tubes 4. The refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of heat transfer tubes 4. The refrigerant flowing through the plurality of heat transfer tubes 4 flows into the merging flow path 3a of the second distributor 3, merges, and flows out to the refrigerant pipe. In the heat exchanger 1, the refrigerant can flow backward, that is, can flow from the second distributor 3 toward the first distributor 2.

<Configuration of first distributor 2>
Hereinafter, the configuration of the first distributor 2 will be described. First, a case where the first distributor 2 is a stacked header will be described as an example.
FIG. 2 is a perspective view in a state where the first distributor 2 is disassembled.

  As shown in FIG. 2, the first distributor 2 has a plate-shaped body 11. The plate-like body 11 is formed by alternately stacking first plate-like members 12_1 to 1st plate-like members 12_4 serving as bare materials and second plate-like members 13_1 to 2nd plate-like members 13_3 serving as clad materials. It is formed. The first plate-shaped member 12_1 and the first plate-shaped member 12_4 are stacked on the outermost side of the plate-shaped body 11 in the stacking direction. Hereinafter, the first plate-shaped member 12_1 to the first plate-shaped member 12_4 may be collectively referred to as a first plate-shaped member 12. Similarly, the second plate member 13_1 to the second plate member 13_3 may be collectively referred to as a second plate member 13.

The first plate member 12 is made of, for example, aluminum. The thickness of the first plate-like member 12 is, for example, about 1 to 10 mm. No brazing material is applied to the first plate member 12. In each of the first plate-like members 12, through-holes 12a_1 to 12a_3 serving as distribution channels 2a are formed. The through holes 12a_1 to 12a_4 penetrate the front and back of the first plate member 12. When the first plate-shaped member 12 and the second plate-shaped member 13 are stacked, the through holes 12a_1 to 12a_3 function as a part of the distribution channel 2a.
The through hole 12a_1 functions as a fluid inlet portion into which the refrigerant flows.
The end of the through hole 12a_3 functions as a fluid outlet from which the refrigerant flows.
Since the through hole 12a_4 functions as the heat transfer tube insertion portion 2b, the refrigerant does not flow.

The second plate-shaped member 13 is made of, for example, aluminum. The thickness of the second plate member 13 is, for example, about 1 to 10 mm, and is formed thinner than the first plate member 12. A brazing material is applied to at least the front and back surfaces of the second plate-shaped member 13. In each of the second plate-like members 13, a through-hole 13a_1 and a through-hole 13a_2 serving as the distribution channel 2a are formed. The through holes 13a_1 to 13a_3 penetrate the front and back of the second plate-shaped member 13. When the first plate-shaped member 12 and the second plate-shaped member 13 are stacked, the through holes 13a_1 and 13a_2 function as a part of the distribution channel 2a.
Since the through-hole 13a_3 functions as the heat transfer tube insertion portion 2b, the refrigerant does not flow.

The through-hole 12a_1 formed in the first plate-shaped member 12_1 and the through-hole 13a_1 formed in the second plate-shaped member 13_1 are formed so as to penetrate in a circular cross section of the flow path. A refrigerant pipe is connected to the through hole 12a_1 functioning as a fluid inlet. For example, a base or the like may be provided on a surface of the first plate-shaped member 12_1 on the inflow side of the refrigerant, and a refrigerant pipe may be connected via the base or the like, or the inner peripheral surface of the through hole 12a_1 may be a refrigerant pipe. The refrigerant pipe may be directly connected to the through hole 12a_1 without using a base or the like.
In addition, the flow path cross section is a cross section obtained by cutting the flow path in a direction orthogonal to the flow of the refrigerant.

  The through-hole 12a_2 formed in the first plate-shaped member 12_2 and the through-hole 12a_3 formed in the first plate-shaped member 12_3 are formed to penetrate, for example, in a Z-shaped cross section of the flow path. The through-hole 12a_2 and the through-hole 12a_3 function as a branch flow path that vertically branches the refrigerant with respect to gravity. The through-hole 13a_1 of the second plate-shaped member 13_1 is formed at a position facing the center of the through-hole 12a_2.

  The through-hole 13a_2 of the second plate-shaped member 13_2 is formed to penetrate, for example, in an elliptical shape (including an elliptical shape) in a flow path cross section. The through-hole 13a_2 functions as an intermediate flow path (crossover flow path) that is not a flow path that branches the refrigerant. That is, the through-hole 13a_2 is located between the through-hole 12a_2 functioning as the upstream branch flow path and the through-hole 12a_3 functioning as the downstream branch flow path located on the fluid outlet side with respect to the upstream branch flow path. That is, the through hole 12a_2 and the through hole 12a_3 are connected so that the refrigerant does not go straight.

Specifically, one end of the through hole 13a_2 of the second plate-shaped member 13_2 is formed at a position facing the end of the through hole 12a_2. The other end of the through hole 13a_2 of the second plate member 13_2 is formed at a position facing the center of the through hole 12a_3. Therefore, the through hole 13a_2 has two ends, that is, an end connected to the through hole 12a_2 (the end 120 illustrated in FIGS. 7 and 8) and an end connected to the through hole 12a_3 (FIG. 7). The end portion 121) shown in FIG. 8 is a position that does not overlap when viewed from the flow direction of the refrigerant, and is formed to extend in the direction of gravity, so that the refrigerant does not travel straight.
In addition, the flow direction of the refrigerant is the flow direction of the refrigerant flowing through the through holes 12a_1 and the through holes 13a_1.

  The through-holes 13a_3 of the second plate-like member 13_3 stacked on the opposite side of the first plate-like member 12_3 from the second plate-like member 13_2 are formed at both ends of the through-hole 12a_3 (the end 130 shown in FIGS. 7 and 8). , End 131).

  When the first plate-like member 12 and the second plate-like member 13 are stacked, adjacent through holes communicate with each other, and the portion other than the communicating through hole adjoins the first plate member 12 or the second plate. The distribution channel 2a is formed by being closed by the shaped member 13.

Further, the through holes 12a_2 and 12a_3 functioning as branch flow paths are located on different layers in the horizontal direction when the first plate member 12 and the second plate member 13 are stacked. .
In the first distributor 2, a case where the distribution channel 2a has four fluid outlets for one fluid inlet is shown as an example, but the number of branches is limited to four. It does not do.
Further, the number of stacked first plate members 12 and second plate members 13 is not limited to the illustrated number.

  As shown in FIG. 2, the through-hole 12a_4 formed in the first plate-shaped member 12_4 and the through-hole 13a_3 formed in the second plate-shaped member 13_3 are formed to face the end of the through-hole 12a_3. , And functions as a heat transfer tube insertion portion 2b into which the distal end portion of the heat transfer tube 4 is inserted. That is, the through-holes 12a_4 and the through-holes 13a_3 are formed on an extension of the heat transfer tube 4 and extend along the outer peripheral surface of the heat transfer tube 4, and the heat transfer tube 4 is inserted into the heat transfer tube 4 here. Are connected to the first distributor 2.

  The inner peripheral surface of the through hole 12a_4 of the first plate member 12_4 is fitted to the outer peripheral surface of the heat transfer tube 4. The fitting should have a gap such that the heated brazing material penetrates by capillary action.

<In the case of a stacked header, the flow of the refrigerant in the first distributor 2>
Hereinafter, the flow of the refrigerant in the first distributor 2 will be described.
FIG. 3 is a development view of the first distributor 2. FIG. 4 is a longitudinal sectional view of the first distributor 2.
3 and 4, the flow direction of the refrigerant is indicated by black arrows. Further, in FIG. 4, for convenience of description, the thickness of the plate-like body is illustrated as being substantially uniform. FIG. 4 shows a cross section cut along the flow direction of the refrigerant.

  As shown in FIGS. 3 and 4, the refrigerant flowing through the refrigerant pipe flows into the first distributor 2 with the through-hole 12a_1 of the first plate-shaped member 12_1 as a fluid inlet. The refrigerant flowing from the through hole 12a_1 flows into the through hole 13a_1 of the second plate-shaped member 13_1.

  The refrigerant flowing from the through hole 12a_1 of the first plate member 12_1 to the through hole 13a_1 of the second plate member 13_1 flows into the center of the through hole 12a_2 of the first plate member 12_2. The refrigerant that has flowed into the center of the through hole 12a_2 of the first plate member 12_2 hits the surface of the second plate member 13_2 that is adjacently stacked, and is branched in two directions (left and right directions). It flows to the end of the through hole 12a_2. The refrigerant that has reached the end of the through hole 12a_2 of the first plate member 12_2 flows into one end of the through hole 13a_2 of the second plate member 13_2.

  The refrigerant flowing into one end of the through hole 13a_2 of the second plate member 13_2 flows to the other end of the through hole 13a_2 of the second plate member 13_2. The refrigerant that has reached the other end of the through hole 13a_2 of the second plate member 13_2 flows into the center of the through hole 12a_3 of the first plate member 12_3.

  The refrigerant that has flowed into the center of the through hole 12a_3 of the first plate member 12_3 hits the surface of the second plate member 13_3 that is stacked adjacently, and branches in two directions (left and right directions), and the first plate member 12_3 It flows to the end of the through hole 12a_3. The end of the through hole 12a_3 of the first plate member 12_3 functions as a fluid outlet, and the refrigerant that has reached the end of the through hole 12a_3 of the first plate member 12_3 transmits the refrigerant located in the through hole 12a_3. The heat flows into the inside of the heat transfer tube 4 from the tip portion 4 a of the heat tube 4.

  The refrigerant that has flowed into the heat transfer tube 4 passes through regions located inside the through holes 13a_3 of the second plate member 13_3 and inside the through holes 12a_4 of the first plate member 12_4, and the fins 5 of the heat transfer tube 4 Flow into the joined area.

<About the through hole 13a_2>
FIG. 5 is an exploded perspective view for explaining the flow of the refrigerant in a conventional distributor (hereinafter, referred to as a distributor 2X) as a comparative example. FIG. 6 is a schematic diagram for explaining the flow of the refrigerant in the distributor 2X. First, the flow of the refrigerant in the distributor 2X will be described with reference to FIGS. In FIGS. 5 and 6, “X” is added to the end of each configuration of the distributor 2X corresponding to the configuration of the first distributor 2 to distinguish it from the configuration of the first distributor 2. . In FIGS. 5 and 6, the flow of the refrigerant is indicated by a broken arrow.

  5 and 6, a portion functioning as a branch flow path including the center of the through hole 12a_2X of the first plate member 12_2X is illustrated as a branch portion 115X, and one end of the through hole 12a_2X of the first plate member 12_2X is illustrated. The portion is illustrated as an end 110X, the other end of the through hole 12a_2X of the first plate-like member 12_2X is illustrated as an end 111X, and the bent flow path portion is illustrated as a bent portion 116X.

  5 and 6, a portion that functions as a branch flow path including the center of the through hole 12a_3X of the first plate member 12_3X is illustrated as a branch portion 135X, and one of the through holes 12a_3X of the first plate member 12_3X. Is illustrated as an end 130X, and the other end of the through hole 12a_3X of the first plate-like member 12_3X is illustrated as an end 131X.

  The refrigerant flowing through the refrigerant pipe flows into the distributor 2X, and flows into the branch 115X of the through hole 12a_2X of the first plate-like member 12_2X. The refrigerant that has flowed into the branch portion 115X hits the surface of the second plate-shaped member 13_2X that is stacked adjacently, branches, and flows to the end 110X and the end 111X of the through hole 12a_2X. The refrigerant in the gas-liquid two-phase state flowing through the bent portion 116X of the through hole 12a_2X functioning as a branch channel is formed by a liquid refrigerant having a high density (the refrigerant W shown in FIG. 6) outside the bent portion 116X of the through hole 12a_2X due to centrifugal force. Sent to That is, the liquid film is biased at the end 110X and the end 111X of the through hole 12a_2X.

  In this state, the refrigerant that has reached the end 110X and the end 111X of the through-hole 12a_2X goes straight through the through-hole 13a_2X of the second plate-shaped member 13_2X, and the downstream first plate-shaped member that functions as a branch flow path. It flows into the through hole 12a_3X of the 12_3X. Therefore, in the through hole 12a_3X of the first plate-like member 12_3X, more liquid refrigerant flows to the side on which the liquid film is biased. In particular, when the liquid film is significantly deflected, it is difficult to divide the distribution ratio of the first plate member 12_3X in the through holes 12a_3X to a predetermined amount (target value), for example, 50%: 50%.

  FIG. 7 is an exploded perspective view for explaining the flow of the refrigerant in the first distributor 2. FIG. 8 is a schematic diagram for explaining the flow of the refrigerant in the first distributor 2. Next, the flow of the refrigerant in the first distributor 2 will be described with reference to FIGS. In FIGS. 7 and 8, the flow of the refrigerant is indicated by broken arrows.

  7 and 8, a portion functioning as a branch flow path including the center of the through hole 12a_2 of the first plate member 12_2 is illustrated as a branch portion 115, and one end of the through hole 12a_2 of the first plate member 12_2. The portion is illustrated as an end 110, the other end of the through hole 12a_2 of the first plate-like member 12_2 is illustrated as an end 111, and the bent channel portion is illustrated as a bent portion 116. Note that the through hole 12a_2 functions as an upstream branch flow path.

  7 and 8, a portion that functions as a branch flow path including the center of the through hole 12a_3 of the first plate member 12_3 is illustrated as a branch portion 135, and one of the through holes 12a_3 of the first plate member 12_3. Is illustrated as an end 130, and the other end of the through hole 12a_3 of the first plate-like member 12_3 is illustrated as an end 131. The through hole 12a_3 functions as a downstream branch flow path.

7 and 8, one end serving as a refrigerant inlet of the through hole 13a_2 of the second plate member 13_2 is illustrated as an end 120, and the refrigerant outlet of the through hole 13a_2 of the second plate member 13_2. The other end that becomes a part is illustrated as an end 121.
In FIG. 8, a portion connecting the end portion 120 and the end portion 121 is illustrated as a virtual line L1, and a portion orthogonal to the portion connecting the end portion 120 and the end portion 121 is illustrated as a virtual line L2. Is shown.

  The refrigerant flowing through the refrigerant pipe flows into the first distributor 2, and flows into the branch portion 115 of the through hole 12a_2 functioning as an upstream branch flow path. The refrigerant that has flowed into the branch portion 115 hits the surface of the second plate-shaped member 13_2 that is stacked adjacently, branches in two directions (left and right directions), and flows to the end 110 and the end 111 of the through hole 12a_2. Like the distributor 2X, the refrigerant in the gas-liquid two-phase state flowing through the bent portion 116 of the through hole 12a_2 functioning as a branch channel has a high density liquid refrigerant (refrigerant W shown in FIG. 8) through the through hole due to centrifugal force. It is moved to the outside of the bent portion 116 of 12a_2. That is, the liquid film is biased at the end portions 110 and 111 of the through hole 12a_2.

In this state, the refrigerant that has reached the end 110 and the end 111 of the through hole 12a_2 flows into the end 120 of the through hole 13a_2 of the second plate-shaped member 13_2 that functions as an intermediate flow path. The refrigerant that has flowed into the end 120 hits the surface of the first plate-like member 12_3 that is stacked adjacently, and the liquid film is scattered. That is, the gas-liquid two-phase refrigerant collides with the flat portion (the surface of the first plate member 12_3) facing the through hole 13a_2, and the liquid film is scattered.
More specifically, the through-hole 13a_2 functioning as an intermediate flow path changes the direction of the refrigerant flowing from the end 120 by applying the refrigerant to the surface of the first plate-like member 12_3 that is adjacently stacked, and then changes the direction of the end 120a. It is designed to be drained from.

  Thereby, the refrigerant flowing through the through-hole 13a_2 eliminates the bias of the liquid film and approaches a gas-liquid two-phase state in which the gas phase and the liquid phase are homogeneously mixed. The refrigerant that has reached the end portion 121 while maintaining this state flows into the through hole 12a_3 that functions as a downstream branch flow path. In other words, the same refrigerant as the through-hole 12a_2 functioning as the upstream branch flow path is also provided in the through-hole 12a_3 functioning as the downstream branch flow path by preventing the refrigerant from flowing straight into the through-hole 12a_3 by the through-hole 13a_2. Can be in a state.

  The through hole 13a_2 only needs to be formed in such a size and shape that the refrigerant flowing from the upstream branch flow path can be changed in direction and then flow out to the downstream branch flow path. For example, in the through hole 13a_2, the flow path length of the portion connecting the end 120 and the end 121 indicated by the virtual line L1 is formed by connecting the end 120 and the end 121 indicated by the virtual line L2. It is preferable that the width is formed to be at least twice as large as the width of the flow path of the portion orthogonal to the existing portion. This allows the refrigerant to flow into the through hole 12a_3 without going straight through the through hole 13a_2.

  Therefore, in the through-hole 12a_3 of the first plate-like member 12_3, the bias of the liquid film is eliminated, and the refrigerant in a nearly homogeneous state flows. Therefore, the distribution ratio in the through hole 12a_3 functioning as the downstream branch flow path can be divided into a predetermined amount (target value), for example, 50%: 50%.

Next, a case where the first distributor 2 is an integrated header will be described as an example.
FIG. 9 is a diagram illustrating the flow of the method of manufacturing the heat exchanger 1. FIG. 10 is a longitudinal sectional view of the first distributor 2 using the lost wax method. First, a method of manufacturing the first distributor 2 using the lost wax method will be described.

  First, in step 0 (not shown), a mold to be the distribution channel 2a of the first distributor 2 is manufactured. In step 1, wax is poured into the mold prepared in step 0 to prepare a wax mold (wax pattern 2a_1) having the same shape as the distribution channel 2a. In step 2, the wax pattern 2a_1 is fixed to the mold 2_1 serving as the first distributor 2, and molten aluminum is poured.

Then, in step 3, the hardened aluminum is heated, and the wax pattern 2a_1 fixed inside the aluminum is melted and poured out. Thereby, the first distributor 2 in which the distribution channel 2a is formed is manufactured. By the steps 0 to 3, the first distributor 2 is completed.
Then, in step 4, the heat exchanger tube 4 is connected to the first distributor 2, and other assembly and processing are performed to complete the heat exchanger 1.

  The first distributor 2 manufactured by the lost wax method does not have the plate-like body 11 as shown in FIG. 10, and the first distributor 2 is configured as a laminated header shown in FIGS. 2 to 4. It is different from the vessel 2. However, each function of the first distributor 2 manufactured by the lost wax method is the same as that of the first distributor 2 configured as a stacked header.

<Flow of refrigerant in first distributor 2 in case of integral header>
Hereinafter, the flow of the refrigerant in the first distributor 2 will be described. FIG. 11 is a longitudinal sectional view showing the flow of the refrigerant in the first distributor 2 completed by the manufacturing method of FIG. In FIG. 11, the same reference numerals are used for components or portions corresponding to the components or portions of the first distributor 2 shown in FIG. Also, in FIG. 11, the correspondence with the plate-like body of the first distributor 2 shown in FIG. 4 is shown using broken lines. Further, in FIG. 11, for the sake of convenience of description, the thickness of the plate-like body is illustrated as being substantially uniform. FIG. 11 shows a cross section cut along the flow direction of the refrigerant. Further, in FIG. 11, the flow direction of the refrigerant is indicated by black arrows.

The basic flow of the refrigerant is the same as the flow of the refrigerant in the first distributor 2 configured as the stacked header described with reference to FIGS. 3 and 4.
The refrigerant flowing through the refrigerant pipe flows into the first distributor 2 with the through hole 12a_1 of the first distributor 2 as a fluid inlet. The refrigerant flowing from the through hole 12a_1 flows through the through hole 13a_1 and flows into the center of the through hole 12a_2. The refrigerant flowing into the center of the through hole 12a_2 branches in two directions (left and right directions) and flows to the end of the through hole 12a_2. The refrigerant that has reached the end of the through hole 12a_2 flows into one end of the through hole 13a_2.

  The refrigerant that has flowed into one end of the through hole 13a_2 flows into the other end of the through hole 13a_2, and flows into the center of the through hole 12a_3. The refrigerant flowing into the center of the through hole 12a_3 branches in two directions (left and right directions) and flows to the end of the through hole 12a_3. The end of the through hole 12a_3 functions as a fluid outlet, and the refrigerant reaching the end of the through hole 12a_3 flows into the inside of the heat transfer tube 4 from the tip 4a of the heat transfer tube 4 located in the through hole 12a_3. I do.

  The refrigerant that has flowed into the heat transfer tube 4 passes through regions located inside the through holes 13a_3 and 12a_4, and flows into a region where the fins 5 of the heat transfer tube 4 are joined.

<Operation and effect of first distributor 2 and heat exchanger 1>
As described above, in the first distributor 2, by forming the through-hole 13a_2 functioning as the branch flow path, the homogeneously mixed gas-liquid two-phase is also formed in the downstream through-hole 13a_2 functioning as the branch flow path. It becomes possible to branch in a state. Therefore, according to the first distributor 2, the bias of the liquid film is eliminated in both the upstream branch flow path and the downstream branch flow path, and the distribution ratio of the refrigerant can be set to a predetermined amount (target value). Distribution performance can be realized.

  In addition, since the heat exchanger 1 includes the first distributor 2, the refrigerant can flow through each path in a homogeneous state, and the heat exchange efficiency is improved.

Embodiment 2. FIG.
A distributor according to Embodiment 2 of the present invention will be described.
In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.
Note that the heat exchanger including the distributor according to the second embodiment is the same as the heat exchanger 1 described in the first embodiment, and a description thereof will be omitted. The distributor according to Embodiment 2 is referred to as a first distributor 2A.

<Configuration of distributor according to Embodiment 2>
Hereinafter, the configuration of the first distributor 2A will be described. Here, a case where the first distributor 2A is a stacked header will be described as an example. However, the first distributor 2A may be an integrated header. In this case, the first distributor 2A may be manufactured with reference to FIG.
FIG. 12 is an exploded perspective view for explaining the flow of the refrigerant in the first distributor 2A. FIG. 13 is a schematic diagram for explaining the flow of the refrigerant in the first distributor 2A. In FIGS. 12 and 13, the flow of the refrigerant is indicated by broken arrows.

  12 and 13, similarly to FIGS. 7 and 8, the branch portion 115, the end portion 110, the end portion 111, the bent portion 116, the branch portion 135, the end portion 130, the end portion 131, the end portion 120, and the end portion. 121 is illustrated.

In the first distributor 2A, the shape of the through hole 12a_3 formed in the first plate member 12_3 is the same as that of the through hole 12a_3 formed in the first plate member 12_3 of the first distributor 2 according to the first embodiment. It is different from the shape.
Specifically, the through-hole 12a_3 has an inflow channel 107 that communicates with an intermediate portion of the branch portion 135 that is formed so as to have a Z-shaped channel cross section. That is, in the same plate (the first plate-shaped member 12_3), the branch portion 135 functioning as a branch channel and the inflow channel 107 through which the refrigerant flows into the branch portion 135 are formed.

  The inflow passage 107 has an end on the fluid inlet side connected to the end 121 of the through hole 13a_2 serving as an intermediate passage, and an end on the fluid outlet side connected to the branch 135, both of which are refrigerant. It is a position that does not overlap when viewed from the flow direction. Therefore, the inflow channel 107 is formed to extend in the direction of gravity. Specifically, as shown in FIG. 12, the end on the fluid inlet side and the end on the fluid outlet side are formed so as to be aligned in the direction of gravity. Note that the middle part of the branch 135 need not be strictly the center of the branch 135.

The end 120 of the through hole 13a_2 is formed at a position facing the end 110 and the end 111 of the through hole 12a_2. Further, the end 121 of the through hole 13a_2 is formed not at the branch portion 135 of the through hole 12a_3 but at a position facing the end of the inflow channel 107.
The through-hole 13a_3 of the second plate-shaped member 13_3 is formed at a position facing the end 130 and the end 131 of the through-hole 12a_3.
Other configurations are the same as in the first embodiment.

<Flow of refrigerant in first distributor 2A>
Next, the flow of the refrigerant in the first distributor 2A will be described.
As shown in FIGS. 12 and 13, the refrigerant flowing into the first distributor 2A flows through the through holes 12a_1 and 13a_1 and flows into the branch portion 115 of the through hole 12a_2 functioning as an upstream branch flow path. . The refrigerant that has flowed into the branch portion 115 hits the surface of the second plate-shaped member 13_2 that is stacked adjacently, branches in two directions (left and right directions), and flows to the end 110 and the end 111 of the through hole 12a_2. The refrigerant that has reached the end 110 and the end 111 of the through hole 12a_2 flows into the end 120 of the through hole 13a_2 of the second plate member 13_2 that functions as an intermediate flow path.

  The refrigerant that has flowed into the end 120 hits the surface of the first plate-like member 12_3 that is stacked adjacently, and the liquid film is scattered. That is, the gas-liquid two-phase refrigerant collides with the flat portion (the surface of the first plate member 12_3) facing the through hole 13a_2, and the liquid film is scattered. Thereby, the refrigerant flowing through the through-hole 13a_2 eliminates the bias of the liquid film and approaches a gas-liquid two-phase state in which the gas phase and the liquid phase are homogeneously mixed. The refrigerant that has reached the end 121 while maintaining this state flows into the end on the fluid inlet side of the inflow passage 107 of the through hole 12a_3 that functions as a downstream branch passage.

  In other words, the same refrigerant as the through-hole 12a_2 functioning as the upstream branch flow path is also provided in the through-hole 12a_3 functioning as the downstream branch flow path by preventing the refrigerant from flowing straight into the through-hole 12a_3 by the through-hole 13a_2. Can be in a state.

  The refrigerant that has flowed into the end of the inflow passage 107 on the fluid inlet side hits the surface of the second plate-shaped member 13_3 that is stacked adjacently, and then flows through the inflow passage 107, and is located on the fluid outlet side of the inflow passage 107. It reaches the end (the end on the connection side with the branch 135), flows into the branch 135, and branches in two directions (left and right directions). The branched refrigerant flows to the ends 130 and 131. The end 130 and the end 131 of the through hole 12a_3 function as a fluid outlet, and the refrigerant that has reached the end 130 and the end 131 of the through hole 12a_3 transmits the refrigerant located in the through hole 13a_3 or the through hole 12a_3. The heat flows into the inside of the heat transfer tube 4 from the tip portion 4 a of the heat tube 4.

  Specifically, the refrigerant in the gas-liquid two-phase state flowing out from the end portion 121 of the through hole 13a_2 functioning as the transfer passage flows into the inflow passage 107 of the downstream through hole 12a_3. At that time, the refrigerant collides with the surface of the second plate member 13_3 facing the through hole 13a_2. Therefore, the gas-liquid two-phase refrigerant becomes more homogeneous from the state homogenized in the through hole 13a_2. Then, the refrigerant flows into the branch portion 135 of the through hole 13a_2, and the refrigerant is distributed.

<Operation and effect of first distributor 2A and heat exchanger 1>
As described above, in the first distributor 2A, in addition to the configuration of the first distributor 2 according to the first embodiment, the inflow channel 107 is provided in the through hole 12a_3 on the downstream side of the through hole 13a_2 functioning as a cross channel. It was provided. That is, in the first distributor 2A, a plurality of collision portions where the refrigerant collides with the plate member are provided. By doing so, the gas phase and the liquid phase of the gas-liquid two-phase refrigerant can be more homogenized, and the distribution ratio in the through-hole 12a_3 can be divided into a predetermined amount (target value), for example, 50%: 50%. Become. Therefore, according to the first distributor 2A, the bias of the liquid film is eliminated in both the upstream branch flow path and the downstream branch flow path, and the distribution ratio of the refrigerant can be set to a predetermined amount (target value). Distribution performance can be realized.

  Further, since the heat exchanger 1 includes the first distributor 2A, the refrigerant can flow in a uniform state in each path, and the heat exchange efficiency is improved.

Embodiment 3 FIG.
A distributor according to Embodiment 3 of the present invention will be described.
In the third embodiment, differences from the first and second embodiments will be mainly described, and the same parts as those in the first and second embodiments will be denoted by the same reference numerals and description thereof will be omitted.
The heat exchanger including the distributor according to the third embodiment is the same as the heat exchanger 1 described in the first embodiment, and a description thereof will not be repeated. The distributor according to Embodiment 3 is referred to as a first distributor 2B.

<Configuration of distributor according to Embodiment 3>
Hereinafter, the configuration of the first distributor 2B will be described. Here, a case where the first distributor 2B is a stacked type header will be described as an example. However, the first distributor 2B may be an integrated header. In this case, the first distributor 2B may be manufactured with reference to FIG.
FIG. 14 is an exploded perspective view for explaining the flow of the refrigerant in the first distributor 2B. FIG. 15 is a schematic diagram schematically showing the shape of the through-hole 12a_3 formed in the first plate-like member 12_3 of the first distributor 2B. In FIG. 14, the flow of the refrigerant is indicated by broken arrows.

  14 and 15, similarly to FIGS. 12 and 13, the branch portion 115, the end portion 110, the end portion 111, the bent portion 116, the branch portion 135, the end portion 130, the end portion 131, the end portion 120, and the end portion. 121, an inflow channel 107 is illustrated.

Although the first distributor 2B has the same basic shape as the first distributor 2A according to the second embodiment, the shape of the through hole 12a_3 formed in the first plate member 12_3 is the same as that of the second distributor. Is different from the shape of the through hole 12a_3 formed in the first plate-like member 12_3 of the first distributor 2A.
That is, the first distributor 2B is different from the second embodiment in that the inflow channel 107 is inclined with respect to the direction of gravity.

Specifically, in the first distributor 2B, the branch portion 135 and the inflow passage 107 are provided in the first plate-like member 12_3, and one end of the inflow passage 107 (the end on the fluid inlet side). Is located in the direction of gravity different from the other end (the end on the fluid outlet side) of the inflow channel 107. More specifically, the refrigerant flow direction of the inflow passage 107 (line X1 shown in FIG. 15) is orthogonal to the refrigerant flow direction (line X2 shown in FIG. 15) of the fluid portion of the branch portion 135 of the through hole 12a_3. Instead, they intersect at a predetermined inflow angle 109.
Other configurations are the same as in the first and second embodiments.

<Flow of refrigerant in first distributor 2B>
Next, the flow of the refrigerant in the first distributor 2B will be described.
As shown in FIGS. 14 and 15, the refrigerant that has flowed into the first distributor 2B flows through the through holes 12a_1 and 13a_1 and flows into the branch portion 115 of the through hole 12a_2 that functions as an upstream branch flow path. . The refrigerant that has flowed into the branch portion 115 hits the surface of the second plate-shaped member 13_2 that is stacked adjacently, branches in two directions (left and right directions), and flows to the end 110 and the end 111 of the through hole 12a_2. The refrigerant that has reached the end 110 and the end 111 of the through hole 12a_2 flows into the end 120 of the through hole 13a_2 of the second plate member 13_2 that functions as an intermediate flow path.

  The refrigerant that has flowed into the end 120 hits the surface of the first plate-like member 12_3 that is stacked adjacently, and the liquid film is scattered. That is, the gas-liquid two-phase refrigerant collides with the flat portion (the surface of the first plate member 12_3) facing the through hole 13a_2, and the liquid film is scattered. Thereby, the refrigerant flowing through the through-hole 13a_2 eliminates the bias of the liquid film and approaches a gas-liquid two-phase state in which the gas phase and the liquid phase are homogeneously mixed. The refrigerant that has reached the end 121 while maintaining this state flows into the end on the fluid inlet side of the inflow passage 107 of the through hole 12a_3 that functions as a downstream branch passage.

  In other words, the same refrigerant as the through-hole 12a_2 functioning as the upstream branch flow path is also provided in the through-hole 12a_3 functioning as the downstream branch flow path by preventing the refrigerant from flowing straight into the through-hole 12a_3 by the through-hole 13a_2. Can be in a state.

  The refrigerant that has flowed into the end of the inflow passage 107 on the fluid inlet side hits the surface of the second plate member 13_3 that is stacked adjacently, and then flows through the inflow passage 107, and the other end of the inflow passage 107. (The end on the connection side with the branch 135), flows into the branch 135, and branches in two directions (left and right directions). The branched refrigerant flows to the ends 130 and 131. The end 130 and the end 131 of the through hole 12a_3 function as a fluid outlet, and the refrigerant that has reached the end 130 and the end 131 of the through hole 12a_3 transmits the refrigerant located in the through hole 13a_3 or the through hole 12a_3. The heat flows into the inside of the heat transfer tube 4 from the tip portion 4 a of the heat tube 4.

  Specifically, the refrigerant in the gas-liquid two-phase state flowing out from the end portion 121 of the through hole 13a_2 functioning as the transfer passage flows into the inflow passage 107 of the downstream through hole 12a_3. At that time, the refrigerant collides with the surface of the second plate member 13_3 facing the through hole 13a_2. Therefore, the gas-liquid two-phase refrigerant becomes more homogeneous from the state homogenized in the through hole 13a_2. Then, the refrigerant flows into the branch portion 135 of the through hole 13a_2, and the refrigerant is distributed.

  At this time, the refrigerant flowing through the inflow passage 107 flows into the branch portion 135 at an inflow angle 109. Therefore, a large amount of the refrigerant flows toward the end 131 of the through hole 12a_3 due to the inertial force. In addition, a vortex 112 is generated at the bent portion of the branch portion 135, and the flow path portion through which the refrigerant flows is narrowed. Due to both of these effects, the flow rate of the refrigerant flowing toward the end 131 increases. The flow rate ratio of the refrigerant flowing through the end portion 130 and the end portion 131 of the branch portion 135 has a linear relationship with the position (inflow angle) between the inflow passage 107 and the branch portion 135, and is controlled by the positional relationship between the two. can do. This can be realized by homogenizing the refrigerant in the gas-liquid phase before the refrigerant reaches the branch portion 135.

<Operation and Effect of First Distributor 2B and Heat Exchanger 1>
As described above, in the first distributor 2B, in addition to the configuration of the first distributor 2A according to Embodiment 2, the inflow passage 107 is inclined with respect to the direction of gravity. That is, in the first distributor 2B, a plurality of collision portions where the refrigerant collides with the plate member are provided, and the distribution ratio can be adjusted. By doing so, the gas phase and the liquid phase of the gas-liquid two-phase refrigerant can be made more uniform, and the distribution ratio in the through-hole 12a_3 can be adjusted to a predetermined amount (target value). Therefore, according to the first distributor 2B, the bias of the liquid film is eliminated in both the upstream branch flow path and the downstream branch flow path, and the distribution ratio of the refrigerant can be set to a predetermined amount (target value). Distribution performance can be realized.

  Further, since the heat exchanger 1 includes the first distributor 2A, the refrigerant can flow in a uniform state in each path, and the heat exchange efficiency is improved.

Embodiment 4 FIG.
A refrigeration cycle apparatus according to Embodiment 4 of the present invention will be described.
<Configuration of refrigeration cycle device 100>
Hereinafter, a schematic configuration of a refrigeration cycle apparatus 100 according to Embodiment 4 will be described.
FIG. 16 is a circuit configuration diagram schematically illustrating an example of a refrigerant circuit configuration of a refrigeration cycle apparatus 100 according to Embodiment 4. In the fourth embodiment, differences from the first to third embodiments will be mainly described, and the same parts as those in the first to third embodiments will be denoted by the same reference numerals and description thereof will be omitted. In FIG. 16, the flow of the refrigerant during the cooling operation is indicated by a broken-line arrow, the flow of the refrigerant during the heating operation is indicated by a solid-line arrow, and the flow of air is indicated by a white arrow.

  The refrigeration cycle apparatus 100 includes, as one of the components, a heat exchanger including the distributor according to any of the first to third embodiments. In addition, for convenience of explanation, the refrigeration cycle apparatus 100 will be described as having the heat exchanger 1 including the first distributor 2 according to the first embodiment. In the fourth embodiment, a case where refrigeration cycle device 100 is an air conditioner will be described as an example.

  The refrigeration cycle apparatus 100 includes a first unit 100A and a second unit 100B as components. The first unit 100A is used as a heat source unit, an outdoor unit, or the like. The second unit 100B is used as an indoor unit or a use-side unit (load-side unit).

  The first unit 100A contains a compressor 101, a flow path switching device 102, a throttle device 104, a second heat exchanger 105, and a blower 105A attached to the second heat exchanger 105. Further, the second heat exchanger 105 includes the first distributor 2. That is, the second heat exchanger 105 is the one to which the heat exchanger 1 described in the first embodiment is applied.

  The second unit 100B houses the first heat exchanger 103 and the blower 103A attached to the first heat exchanger 103. In addition, the first heat exchanger 103 includes the first distributor 2. That is, the first heat exchanger 103 is the one to which the heat exchanger 1 described in the first embodiment is applied.

  Then, as shown in FIG. 16, the compressor 101, the first heat exchanger 103, the expansion device 104, and the second heat exchanger 105 are connected by a refrigerant pipe 106 to form a refrigerant circuit. The blower 103A is attached to the first heat exchanger 103 and supplies air to the first heat exchanger 103. The blower 105A is attached to the second heat exchanger 105 and supplies air to the second heat exchanger 105.

  The compressor 101 compresses a refrigerant. The refrigerant compressed by the compressor 101 is discharged and sent to the first heat exchanger 103 or the second heat exchanger 105. The compressor 101 can be composed of, for example, a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor, and the like.

  The flow path switching device 102 switches the flow of the refrigerant between a heating operation and a cooling operation. That is, the flow path switching device 102 is switched to connect the compressor 101 and the first heat exchanger 103 during the heating operation, and to connect the compressor 101 and the second heat exchanger 105 during the cooling operation. Can be switched. Note that the flow path switching device 102 may be configured with, for example, a four-way valve. However, a combination of a two-way valve or a three-way valve may be adopted as the flow path switching device 102.

  The first heat exchanger 103 functions as a condenser during the heating operation and functions as an evaporator during the cooling operation. That is, when functioning as a condenser, the first heat exchanger 103 exchanges heat between the high-temperature and high-pressure refrigerant discharged from the compressor 101 and the air supplied by the blower 103A, and condenses the high-temperature and high-pressure gas refrigerant. . On the other hand, when functioning as an evaporator, the first heat exchanger 103 exchanges heat between the low-temperature and low-pressure refrigerant flowing out of the expansion device 104 and the air supplied by the blower 103A to form a low-temperature and low-pressure liquid refrigerant or a two-phase liquid refrigerant. The refrigerant evaporates.

  The expansion device 104 expands the refrigerant flowing out of the first heat exchanger 103 or the second heat exchanger 105 to reduce the pressure. The expansion device 104 may be composed of, for example, an electric expansion valve that can adjust the flow rate of the refrigerant. As the expansion device 104, not only an electric expansion valve but also a mechanical expansion valve employing a diaphragm in a pressure receiving portion, a capillary tube, or the like can be applied.

  The second heat exchanger 105 functions as an evaporator during the heating operation and functions as a condenser during the cooling operation. That is, when functioning as an evaporator, the second heat exchanger 105 exchanges heat between the low-temperature and low-pressure refrigerant flowing out of the expansion device 104 and the air supplied by the blower 105A, and forms a low-temperature and low-pressure liquid refrigerant or a two-phase liquid refrigerant. The refrigerant evaporates. On the other hand, when functioning as a condenser, the second heat exchanger 105 exchanges heat between the high-temperature and high-pressure refrigerant discharged from the compressor 101 and the air supplied by the blower 105A, and condenses the high-temperature and high-pressure gas refrigerant. .

<Operation of refrigeration cycle device 100>
Next, the operation of the refrigeration cycle apparatus 100 will be described together with the flow of the refrigerant. Here, the operation of the refrigeration cycle apparatus 100 will be described by taking as an example a case where the heat exchange fluid is air and the heat exchange fluid is a refrigerant.

  First, the cooling operation performed by the refrigeration cycle apparatus 100 will be described. The flow of the refrigerant during the cooling operation is indicated by a broken arrow in FIG.

  As shown in FIG. 16, by driving the compressor 101, a high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 101. Hereinafter, the refrigerant flows according to the dashed arrows. The high-temperature and high-pressure gas refrigerant (single phase) discharged from the compressor 101 flows into the second heat exchanger 105 functioning as a condenser via the flow path switching device 102. In the second heat exchanger 105, heat exchange is performed between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the blower 105A, and the high-temperature and high-pressure gas refrigerant is condensed to generate a high-pressure liquid refrigerant ( Single phase).

  The high-pressure liquid refrigerant sent from the second heat exchanger 105 is converted into a two-phase refrigerant of a low-pressure gas refrigerant and a liquid refrigerant by the expansion device 104. The refrigerant in the two-phase state flows into the first heat exchanger 103 functioning as an evaporator. The first heat exchanger 103 includes the first distributor 2, and the first distributor 2 distributes the refrigerant according to the number of passes of the first heat exchanger 103 to form the first heat exchanger 103. Into the heat transfer tube 4.

  In the first heat exchanger 103, heat exchange is performed between the flowing two-phase refrigerant and the air supplied by the blower 103A, and the liquid refrigerant among the two-phase refrigerant evaporates and has a low pressure. It becomes a gas refrigerant (single phase). The low-pressure gas refrigerant sent from the first heat exchanger 103 flows into the compressor 101 via the flow switching device 102, is compressed into a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 101 again. Thereafter, this cycle is repeated.

  Next, a heating operation performed by the refrigeration cycle apparatus 100 will be described. The flow of the refrigerant during the heating operation is indicated by solid arrows in FIG.

  As shown in FIG. 16, by driving the compressor 101, a high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 101. Hereinafter, the refrigerant flows according to solid arrows. The high-temperature and high-pressure gas refrigerant (single phase) discharged from the compressor 101 flows into the first heat exchanger 103 functioning as a condenser via the flow path switching device 102. In the first heat exchanger 103, heat exchange is performed between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the blower 103A, and the high-temperature and high-pressure gas refrigerant is condensed to generate a high-pressure liquid refrigerant ( Single phase).

  The high-pressure liquid refrigerant sent from the first heat exchanger 103 is turned into a two-phase refrigerant of a low-pressure gas refrigerant and a liquid refrigerant by the expansion device 104. The refrigerant in the two-phase state flows into the second heat exchanger 105 functioning as an evaporator. The second heat exchanger 105 includes the first distributor 2, and the first distributor 2 distributes the refrigerant according to the number of passes of the second heat exchanger 105 to form the second heat exchanger 105. Into the heat transfer tube 4.

  In the second heat exchanger 105, heat exchange is performed between the two-phase refrigerant that has flowed in and the air supplied by the blower 105A, and the liquid refrigerant among the two-phase refrigerant evaporates and has a low pressure. It becomes a gas refrigerant (single phase). The low-pressure gas refrigerant sent from the second heat exchanger 105 flows into the compressor 101 via the flow path switching device 102, is compressed into a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 101 again. Thereafter, this cycle is repeated.

As described above, in the refrigeration cycle apparatus 100, the first distributor 2 is provided on the upstream side of the first heat exchanger 103 and the second heat exchanger 105.
Therefore, according to the refrigeration cycle apparatus 100, the refrigerant can flow in a uniform state in each path in the first heat exchanger 103 and the second heat exchanger 105, and the performance of the heat exchanger can be maximized. It becomes possible and the heat exchange efficiency is improved.

  Here, the case where both the first heat exchanger 103 and the second heat exchanger 105 are provided with the heat exchanger according to any one of the first to third embodiments has been described as an example. At least one of the heat exchanger 103 and the second heat exchanger 105 may include the heat exchanger according to any of the first to third embodiments.

The refrigerant used in the refrigeration cycle device 100 is not particularly limited, and the effect can be exerted even if a refrigerant such as R410A, R32, HFO1234yf is used.
Although examples of the working fluid include air and refrigerant, the present invention is not limited to this, and similar effects can be obtained by using another gas, liquid, or gas-liquid mixed fluid. That is, the working fluid changes, and in any case, the effect is achieved.
Further, as other examples of the refrigeration cycle device 100, there are a water heater, a refrigerator, an air conditioning and hot water supply combined machine, and in any case, it is possible to maximize the performance of the heat exchanger, The heat exchange efficiency is improved.

  DESCRIPTION OF SYMBOLS 1 Heat exchanger, 2 1st distributor, 2A 1st distributor, 2B 1st distributor, 2X distributor, 2_1 mold, 2a distribution channel, 2a_1 wax pattern, 2b heat transfer tube insertion part, 3rd distribution Vessel, 3a merging channel, 4 heat transfer tube, 4a tip, 5 fin, 11 plate, 12 first plate, 12_1 first plate, 12_2 first plate, 12_2X first plate , 12_3 1st plate member, 12_3X 1st plate member, 12_4 1st plate member, 12a_1 through hole, 12a_2 through hole, 12a_2X through hole, 12a_3 through hole, 12a_3X through hole, 12a_4 through hole, 13 second plate Member, 13_1 second plate member, 13_2 second plate member, 13_2X second plate member, 13_3 second plate member, 13a_1 through hole, 13a_2 through hole , 13a_2X through hole, 13a_3 through hole, 100 refrigeration cycle device, 100A first unit, 100B second unit, 101 compressor, 102 flow path switching device, 103 first heat exchanger, 103A blower, 104 expansion device, 105th 2 heat exchanger, 105A blower, 106 refrigerant pipe, 107 inflow passage, 109 inflow angle, 110 end, 110X end, 111 end, 111X end, 112 vortex, 115 branch, 115X branch, 116 bend Part, 116X bent part, 120 end, 121 end, 130 end, 130X end, 131 end, 131X end, 135 branch, 135X branch, L1 virtual line, L2 virtual line, W refrigerant.

The distributor according to the present invention is a distributor that distributes a fluid flowing from a fluid inlet to a plurality of fluid outlets, and includes an upstream branch flow path and the plurality of fluid outlets more than the upstream branch flow path. A plurality of branch flow paths having a downstream branch flow path on the side of the section, and the upstream branch flow path and the downstream branch flow path are located between the upstream branch flow path and the downstream branch flow path. An intermediate flow path connecting the flow path, and the fluid is configured to flow in one direction from the fluid inlet toward the plurality of fluid outlets . One end connected to the upstream branch flow path, and the other end connected to the downstream branch flow path, the flow of the fluid flowing from the one end , Without changing the direction and then flowing out from the other end.

Claims (10)

A distributor for distributing fluid flowing from a fluid inlet to a plurality of fluid outlets,
An upstream branch flow path, and a plurality of branch flow paths having a downstream branch flow path closer to the plurality of fluid outlets than the upstream branch flow path,
An intermediate flow path that is between the upstream branch flow path and the downstream branch flow path and connects the upstream branch flow path and the downstream branch flow path,
The intermediate flow path,
One end connected to the upstream branch flow path, and the other end connected to the downstream branch flow path,
A distributor that changes the direction of the flow of the fluid that has flowed in from the one end and then flows out of the other end. The intermediate flow path,
The flow path length of the portion connecting the one end and the other end,
2. The distributor according to claim 1, wherein the width of the flow path is at least twice as large as a flow path width of a part orthogonal to a part connecting the one end and the other end. 3. The downstream branch flow path,
A branch portion for branching the fluid in two directions;
An inflow channel communicating with the intermediate portion of the branch portion,
The inflow channel,
An end on the fluid inlet side connected to the other end of the intermediate flow path, and an end on the fluid outlet side connected to the branch portion,
The distributor according to claim 1, wherein the flow of the fluid that has flowed in from the end on the fluid inlet side is changed in direction and then flows out from the other end. The inflow channel,
The distributor according to claim 3, wherein the end on the fluid inlet side and the end on the fluid outlet side are formed so as to be aligned in the direction of gravity. The inflow channel,
The distributor according to claim 3, wherein the end on the fluid inlet side and the end on the fluid outlet side are formed so as to be located in different directions of gravity. The inflow channel,
The flow direction of the fluid flowing through the fluid inlet side end and the fluid outlet side end,
The distributor according to claim 5, wherein a portion connected to the end on the fluid outlet side is not orthogonal to a flow direction of the fluid flowing through the branch portion. The fluid inlet, the branch flow path, and the plurality of fluid outlets,
The distributor according to any one of claims 1 to 6, wherein the distributor is formed by stacking a plurality of plate-like bodies each having a through hole. A distributor according to any one of claims 1 to 7,
A plurality of heat transfer tubes into which the fluid flowing out of the plurality of fluid outlets of the distributor flows,
With a heat exchanger. The heat exchanger according to claim 8, wherein the plurality of heat transfer tubes are circular tubes or flat tubes. A refrigeration cycle device comprising the heat exchanger according to claim 8 or 9 as at least one of an evaporator and a condenser.

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